Control valve



Dec. 19, 1967 J. E. PAPIN I 3,359,043

CONTROL VALVE Filed Aug. 24, 1966 2 Sheets-Sheet l 2 FIG. 1

RES.

SERVICE LINE T V TRACTOR PROTECTOR 8 J CK 26 VALVE RESI U 20 5 J l6 l7 4 CONTROL LINE T0 7 TRACTOR PROTECTOR VALVE r EMERGENCY LINE T0 5 TRACTOR PROTECTOR VALVE FIG. 3

INVENTOR 29 JOSEPH E- PAPI 4s 2 ,9), Z W

Dec. 19, 1967 J. E. PAPIN 3,359,043

CONTROL VALVE Filed Aug. 24, 1966 '2 Sheets-Sheet 2 48 INVENTOR I JOSEPH E. PAPIN FIG. 2

United States Patent 3,359,043 CONTROL VALVE Joseph E. Papin, Florissant, Mo., assignor, by mesne assignrnents, to Tung-Sol Electric Inc., Newark, N.J., a corporation of Delaware Filed Aug. 24, 1966, Ser. No. 574,634 11 Claims. (Cl. 303-52) This invention relates to tandem control valves and in particular to those having force responsive primary application means and fluid pressure responsive secondary application means.

In the past, tandem control valves were provided having a primary or manually actuated piston movable to actuate a primary valve element for establishing a primary fluid pressure in the primary branch of a dual fluid pressure system, and said tandem control valves were also provided with split secondary or relay pistons having abutment means therebetween to eflect concerted move ment of both of said split secondary pistons in response to the established primary fluid pressure wherein only one of said split secondary pistons engaged and actuated a secondary valve element to establish a secondary fluid pressure in the secondary branch of said dual fluid pressure system. In addition, the primary piston was also provided with spring driven means for automatically actuating the primary valve element and for driving the aforementioned one split secondary piston to actuate the secondary valve element when the fluid pressure in the system was reduced to a predetermined minimum due to leaks or the like. One of the undesirable or disadvantageous features of such past control valves was that the automatic actuation of the aforementioned spring driven means was opposed by the return spring acting against the one split secondary piston. Another undesirable or disadvantageous feature of such past control valves was that the aforementioned one split secondary piston also was provided with a reaction area responsive to the fluid pressure established by the automatic actuation of the aforementioned spring driven means to create a reaction force opposing the automatic actuation of said spring driven means. And still another disadvantageous or undesirable feature is that none of such known prior art control valves provides completely independent actuation of the secondary valve element by both of the aforementioned split secondary pistons.

The primary object of the present invention is to provide novel control valve means for use in a dual fluid pressure system which overcomes the aforementioned undesirable or disadvantageous features.

This, as well as other objects and advantageous features of the present invention, will become apparent hereinafter.

Briefly, the present invention embodies a control valve having a pair of pressure fluid flow passages therethrough, means movable to establish pressure fluid flow through one of said flow passages, a pair of independently movable application means respectively controlling the other of said flow passages, one of said application means being movable independently of the other of said application means in response to the established fluid pressure in said one flow passage to establish pressure fluid flow through the other of said flow passages, and said other application means being driven independently of said one application means in response to movement of said movable means to also establish pressure fluid flow through said other flow passage in the event of fluid pressure failure in said one flow passage.

In the drawings which illustrate embodiments of the invention,

FIG. 1 is a diagrammatic view of a dual fluid pressure system having tandem control valve means therein embodying the present invention,

FIG. 2 is an enlarged sectional view showing the tandem control valve means of FIG. 1 in cross-section, and

FIG. 3 is an enlarged sectional view showing another tandem control valve means for use in the system of FIG. 1 and embodying the present invention in cross-section.

Referring now to the drawings and in particular to FIG. 1 thereof, a dual or separate fluid pressure system 1, such as that utilized on the tractor of a tractor-trailer vehicle combination, is shown having fluid pressure generating means, such as a compressor 2, connected with a system or main reservoir 3 by a conduit 4, and an emergency line 5 is connected between said main reservoir and the emergency port of a tractor protector valve (not shown) of the type well known to the art, such as that disclosed in US. Patent No. 2,859,762, issued Nov. 11, 1959, to Cyril B. Fites, said emergency line being adapted for operative connection through said tractor protector valve with the emergency portion of the usual trailer braking system, also well known in the art, as illustrated in the aforementioned patent. The system 1 is also pro vided with separate fluid pressure branches, indicated generally at 6 and 7, for connection with separate axle sets of wheel brake assemblies (not shown) on said tractor. The branch 6 includes a conduit 8 connected in parallel circuit relation between the emergency line 5 and one of a pair of separate inlet ports of a treadle operated tandem control or application valve 9 having a branch or protected reservoir 10 interposed therein, and a unidirectional check valve 11 is connected in the conduit 8 to provide for uni-directional pressure fluid flow from said main reservoir to said protected reservoir. The control valve 9 is also provided with a pair of separate outlet ports, and a tractor service line or conduit 12 connects one of said outlet ports with a fluid pressure responsive motor or brake chamber 13 which is operatively connected with linkage means, such as a slack adjustor 14, to control the energization of a friction device or wheel brake assembly on one tractor axle (not shown). The branch 7 includes a conduit 15 connected in parallel circuit relation between the emergency line 5 and the other of the inlet ports of the control valve 9 having another branch or protected reservoir 16 interposed therein, and a uni-directional check valve 17 is connected in the con-' duit 15 to provide for uni-directional pressure fluid flow from the main reservoir to the protected reservoir 16. Another tractor service line or conduit 18 is connected between the other of the outlet ports of the control valve 9 and another fluid pressure responsive motor or brake chamber 19 which is operatively connected with linkage means, such as slack adjustor 20, to control the energization of another friction device or wheel brake assembly on another tractor axle (not shown). A two-way valve 21 is connected between the tractor service lines 12, 18 to provide pressure fluid flow from either thereof to another conduit or service line 22 which is connected with the service port of the aforementioned tractor protector valve, said service line 22 being adapted for operative connection through said tractor protector valve with the service portion of the aforementioned, usual, trailer braking system. Another conduit 23 is connected between the main reservoir 3 and a control or emergency port of the control valve 9, and a push-pull hand valve 24 of a type Well known to the art is interposed in said conduit 23, said push-pull valve being manually operable between a charging position connecting said control port in pressure fluid communication with said main reservoir and a venting position interrupting pressure fluid communication between said control port and main reservoir and venting said control port to the atmosphere. To complete the description of the system 1, another conduit 25 is connected between the main reservoir 3 and the control port or portion of the aforementioned tractor protector valve having another push-pull hand valve 26 interposed therein, said push-pull valve 26 being similar to the push-pull valve 24 and being manually operable between a charging position connecting said main reservoir in pressure fluid communication with the control portion of said tractor protector valve to thereby effect open pressure fluid communicaton between the service and emergency lines 22, of the tractor and those of the aforementioned, usual, trailer braking system and a venting position for venting the control portion of said tractor protector valve to the atmosphere thereby interrupting the pressure fluid communication between the service and emergency lines 22, 5 of the tractor and those of the trailer braking systems.

The control valve 9, FIG. 2, is provided with upper, intermediate and lower housings 27, 28 and 29 and a closure member 30 for said upper housing having a guide opening 31 therethrough to receive the force transmitting linkage of an operator controlled treadle or lever. (not shown), said housings and closure member being interconnected by suitable means, such as studs 32.

The upper housing 27 is provided with a bore 33 defining an annular wall or partition 34 axially positioned between counterbores 35, 36, said counterbore 35 forming an inlet chamber. Inlet and outlet ports 37, 38, which receive the conduits 8, 12, as previously mentioned, are provided in the upper housing 27 connecting with the counterbores 35, 36, respectively, and a control port 39 is also provided in said upper housing 27 connecting with the counterbore 36 between the outlet port 38 and the open end of said counterbore.

The lower housing 29 is provided with a bore 41 defining an annular wall or partition 42 axially positioned between counterbores 43, 44, said counterbore 43 forming an inlet chamber. Another inlet and outlet port 45, 46 which receive conduits 15, 18, as previously mentioned, are provided in the lower housing 29 connecting with counterbores 43, 44, respectively. A valve guide member 47 is provided with a bore 48 therethrough in which is disposed a seal 49, and said valve guide member is threadedly received in the lower end of the counterbore 43. An inlet valve 50 is also provided with an axial bore or exhaust opening 51 therethrough and is slidably received in the valve guide member bore 48 in sealing engagement with the seal 49. A valve spring 52 is biased between the valve element 50 and the valve guide member 47 normally urging said valve element into sealing engagement with a valve seat 53 which is formed on the wall 42 in circumscribing relation with the housing bore 41. The inlet and outlet ports 37, 38 form one separate set of ports in the upper housing 27 and the inlet and outlet ports 45, 46 form another separate set of ports in the lower housing 29.

An application member or relay piston 54 having a peripheral seal 55 disposed therein is slidably received in the counterbore 44 being normally urge toward abutting engagement with the intermediate housing 28 by a return spring 56 interposed between the housing wall 42 and said relay piston. The relay piston 54 is provided with an integral extension 57 having a valve seat 58 in the free end thereof for operative engagement with the valve element 50. A bore 59 having a seal 60 disposed therein is axially provided through the relay piston and extension 54, 57 and is substantially concentric with the extension valve seat 58. An application chamber 61 is defined in the counterbore 44 between the upper end or side of the relay piston 54 and the intermediate housing 28, and a passageway 62 is provided through the upper and intermediate housings 27, 28 connected between said application chamber and the counterbore 36 in open pressure fluid communication with the outlet port 38. An outlet chamber 62a connected in open pressure fluid communication with the outlet port 46 is also. defined in the counterbore 44 between the housing wall 42 and the lower end or side of the relay piston 54, said upper and lower sides of said relay piston respectively defining opposed equal effective areas A A Another valve element 63 having a bore or passage 64. therethrough is normally urged by a valve spring 65 into sealing engagement with a valve seat 66 formed on the housing wall 34 in circumscribing relation with the housing bore 33 to interrupt pressure fluid communication between the inlet and outlet ports 37, 38. The intermediate housing 28 is provided with a bore 67 having a seal 68 disposed therein, said bore 67 being substantially coaxial with the relay piston bore 59 and the valve element bore 64.

An application member or reaction piston, indicated generally at 69, is slidably received in the housing counterbore 36 between the outlet and control ports 38, 39 defining with the housing wall portion 34 an outlet chamber 70 in open pressure fluid communication with said outlet port, and a return spring 71 is interposed between the Wall 34 and said reaction piston normally urging said reaction piston toward abutment with the closure member 30. Spaced seals 72, 73 are carried in the reaction piston 69 in sealing engagement with the housing counterbore 36, and a peripheral groove 74 is provided in said reaction piston between said seals in open pressure fluid communication with the control port 39 at all times. Axially stepped bores 75, 76 are provided through the reaction piston 69' having a radial shoulder 77 formed therebetween, and a seal 78 is disposed in the smaller stepped bore 76. Snap ring and groove assemblies 79, 80 are respectively provided adjacent the mid-portion and upper end of the large stepped bore 75, and a pre-compressed metering spring and retainer assembly 81 is slidably contained within said larger stepped bore 75 in abutment with said snap rings 79, 80. An emergency or control piston 82 is slidably received in the larger stepped bore 75 having a peripheral seal 83 in sealing engagement therewith, and said control piston isprovide with an integral extension 84 slidably received in the smaller stepped bore 76 in sealing engagement with the seal 78. An expansible emergency or control chamber 85 is defined in the larger stepped bore 75 between the control piston 82 and the reaction piston shoulder 77, and a passage 86 is provided in the reaction piston 69 in open pressure fluid communication between the reaction piston peripheral groove 74 and said control chamber. The lower end of the extension 84 extends into the outlet chamber 70 having a valve seat 87 thereon for operative engagement with the valve element 63, and an emergency spring 88 has one end connected with the control piston 82 and the other end thereof contained by a cup-shaped retainer 89 urging said retainer into displacement preventing engagement with the snap ring 79.

An emergency member 90 which is slidably received in the valve element bore 64, the intermediate housing bore 67, and the relay piston bore 59, said emergency member having opposed eflective areas A A, which are substantially balanced and subjected to the atmosphere. The upper end of the emergency member is drivingly connected or integrally formed with the control piston extension 84 and a valve seat 91 is defined on the lower or free end of said emergency member for operative engagement with the valve element 50. An exhaust passage 92 is axially provided through the emergency member 90 extending through the valve seat 91, and a crosspassage or exhaust passage 93 is provided through the emergency member 90 connecting with the exhaust passage 92 adjacent to the valve seat 87 of the control piston extension 84 to normally vent the outlet port 38 to atmosphere.

Under normal operating conditions with the push-pull valves 24, 26 in the charging positions thereof, fluid pressure generated by the compressor 2 flows through the conduit 4, the main reservoir 3, and the conduit and push-pull valve 23, 24 into the control port 39 of the control valve 9 and therefrom through the reaction piston peripheral groove and passage 74, 86 into the control chamber 85. The fluid pressure so established in the control chamber 85 acts on the effective area of the control piston 32 therein to establish an emergency force acting against the compressive force of the emergency spring 88 to move said emergency piston upwardly in the reaction piston bore 75 to its inoperative position in abutting engagement with the spring retainer 89 and the snap ring 79. The fluid pressure so generated by the compressor 2 also flows from the main reservoir 3 through the control line and push-pull valve 25, 26 to the control portion of the tractor protector valve and also through the emergency line 5 to the emergency portion of the tractor protector valve. From the emergency line 5, the fluid pressure flows through the conduit 8, the uni-directional valve 11 and protected reservoir of the system branch 6 into the inlet port 37 of the control valve 9 and therefrom into the inlet chamber 35, and fluid pressure also flows from said emergency line through the conduit 15, the uni-directional valve 17 and protected reservoir 16 of the system branch 7 into the inlet port 45 of the control valve 9 and therefrom into the inlet chamber 43. From the foregoing, it is apparent that the reservoirs 10, 16 are protected reservoirs since the unidirectional valves 11, 17 protect said reservoirs against loss of fluid pressure therefrom due to a malfunctioning compressor and/or leaks or the like in the system 1 ahead of the reservoirs 10, 16. With the fluid pressure so established in the protected reservoirs 10, 16 and the emergency chamber 85 of the control valve 9, the component parts of said control valve are now positioned as shown in FIG. 2.

If the operator desires to effect a braking application under normal operating conditions, a manually applied force on the metering spring assembly 81 concertedly moves the reaction piston 69 downwardly against the compressive force of the return spring 71. It should be noted that the emergency member 90 is concertedly movable with the reaction piston 59 and completely independent of the relay piston 54. This downward movement initially engages the valve seat 87 of the control piston 82 with the inlet valve 63 closing the exhaust passage 93 and isolating the outlet chamber 70 from the atmosphere. Further downward movement of the reaction piston 69 urges the inlet valve 63 against the valve spring 65 to a position disengaged from the valve seat 66 to establish pressure fluid communication between the inlet and outlet ports 37, 38. The pressure fluid flows in the system branch 6 from the inlet port 37 through the inlet chamber 35, the connecting passage 33, the outlet chamber 70 and the outlet port 38 into the service line 12 to actuate the brake chamber 13 which, in turn, rotates the slack adjustor 14 to energize the wheel brake assembly associated therewith. At the same time, the pressure fluid so established in the outlet chamber 70 also flows therefrom through the housing passage 62 into the application chamber 61 and acts on the effective area A of the relay piston 54 to create an application force which moves said relay piston independently of the emergency member 90 against the return spring 56 to engage the valve seat 58 with the inlet valve 50 thereby closing the inlet valve exhaust opening 51 and isolating the outlet chamber 62a from the atmosphere. Further downward movement of the relay piston 54 moves the inlet valve 50 against the valve spring 52 to a position disengaged from the valve seat 53 and establishing pressure fluid communication between the inlet and outlet ports 45, 46. Pressure fluid also flows in the system branch 7 from the inlet port 45 through the inlet chamber 43, the connecting passage 41, the outlet chamber 62a and the out let port 46 into the service line 18 to actuate the brake chamber 19 which, in turn, rotates the slack adjustor 20 to energize the wheel brake assembly associated therewith. Of course, the two-way valve 21 functions in response to applied fluid pressure in either of the service lines 12, 18 to provide passage thereof through the conduit 22 to the service portion of the tractor protector valve to effect service energization of the trailer brake system in the usual manner.

When the reaction force created by the established fluid pressure in the outlet chamber 71) acting on the effective area of the reaction piston 69 equals the manually applied force, said reaction piston is moved upwardly against the metering spring assembly 81 wherein the inlet valve 63 is positioned in lapped engagement with the housing valve seat 66 and the control piston valve seat 87 is positioned in lapped engagement with said inlet valve. The reaction force acting through the metering spring 81 against the manually applied force affords the operator a direct and accurate feel as to the extent of the braking effort or application. Similarly, when the reaction force created by the established fluid pressure in the outlet chamber 62a acting on the effective area A of the relay piston 54 equals the application force, said relay piston is also moved upwardly wherein the inlet valve 50 is positioned in lapped engagement with the housing valve seat 53 and the relay piston valve seat 58 is positioned in lapped engagement with said inlet valve. If greater braking application is desired, the manually applied force is increased which results in increased application force, and the component parts of control valve 9 function in the same manner, as previously described, to again move said component parts to their lapped positions.

When the desired braking effort is attained, the manually applied force is removed from the reaction piston 69 and the return springs 65, 70 move the valve element 63 and said reaction piston upwardly to their original positions. Since the valve element 63 is sealably engaged with the housing valve seat 66 to interrupt pressure fluid communication between inlet and outlet ports 37, 38, the upward movement of the reaction piston 69 disengages the control piston valve seat 87 from said valve element to re-establish communication between the outlet port 33 and the atmosphere and de-energize the wheel brake assemblies associated therewith by exhausting fluid pressure from the brake chamber 13 through the service line 12, said outlet port, the outlet chamber 70, and the emergency member exhaust passages 92, 93. At the same time, the fluid pressure is also exhausted from the application chamber 61 through the housing passage 62 into the outlet chamber 70 and therefrom to the atmosphere, as previously described, to eliminate the application force on the relay piston 54. Upon the elimination of the application force, the compressive forces of the return springs 52, 56 move the valve element 50 and the relay piston 54 upwardly to their original positions. Since the valve element 50 is sealably engaged with the housing valve seat 53 to interrupt pressure fluid communication between the inlet and outlet ports 45, 46, the upward movement of the relay piston 54 disengages the valve seat 58 thereof from the valve element 50 to re-establish communication between the outlet port 46 and the atmosphere and de-energize the wheel brake assembly associated therewith by exhausting fluid pressure from the brake chamber 19 through the service line 13, said outlet port, the outlet chamber 62a, and the valve member exhaust passage 51. Of course, the two-way valve 21 functions to provide simultaneous exhaustion of the service line 22 to either of the tractor service lines 12, 18, thereby also effecting exhaustion of the service portions of the trailer braking system in the usual manner.

Under emergency conditions when the fluid pressure in the main reservoir 3 is reduced or lost due to a malfunctioning compressor and/ or leaks or the like in the system 1 ahead of the protected reservoirs 10, 16, the fluid pressure in the emergency chamber of the control valve 9 is correspondingly reduced, along with the the emergency force acting on the emergency piston 82. When the fluid pressure in the emergency chamber 85 is so reduced to a predetermined minimum value, the compressive force of the emergency spring 88 overcomes the opposing reduced emergency force and moves the emergency piston 82 downwardly in the reaction piston bores 75, 76 relative to the reaction piston 69 to engage the emergency piston valve seat 87 with the valve element 63 closing the exhaust passages 92, 93. Further independent downward movement of the emergency piston 82 by the emergency spring 88 disengages the inlet valve 63 from the housing valve seat 66 to automatically establish pressure fluid communication between the inlet and outlet ports 37, 38, and the relay piston 54 is also movable independently of the emergency member 90 in response to the fluid pressure automatically established in the outlet chamber 70 and the application chamber 61 to engage and move the inlet valve 50 to a position disengaged from the housing valve seat 53 thereby automatically establishing pressure fluid communication between the inlet and outlet ports 45, 46, as previously described hereinabove. Since the protected reservoirs 10, 16 are protected against a depletion or reduction of the fluid pressure therein by the uni-directional check valves 11, 17 when the fluid pressure in the main reservoir 3 is reduced or depleted, it is obvious that such energization of the wheel brake assemblies under these emergency conditions is effected under full reservoir pressure from the protected reservoirs 10, 16.

In the event that the operator treadle or treadle linkage (not shown) is lost, broken, disengaged from the control valve 9 or for some other reason becomes inoperative for transmitting the applied force to the reaction piston 69, the operator can manually actuate the system 1 to effect or simulate emergency conditions by manually moving the push-pull valve 24 to the venting position thereof to interrupt pressure fluid communication between the main reservoir 3 and the emergency port 39 of the control valve 9 and exhaust said emergency port to the atmosphere. When the system 1 is manually actuated in this manner to effect an emergency condition, fluid pressure in the emergency chamber 85 is vented to the atmosphere through the reaction piston peripheral groove and passage 74, 86, the emergency port 39 and the conduit 23 through the push-pull valve 24. Exhaustion of the fluid pressure from the emergency chamber 85 eliminates the emergency force on the emergency piston 82 thereby permitting the opposing force of the emergency spring 88 to move said emergency piston relative to the reaction piston 69 and effect automatic actuation of the valve element 63 under emergency conditions, and the relay piston 54 is also automatically movable independently of the emergency member 90 in response to the fluid pressure established in the application chamber 61 under such emergency conditions to actuate the inlet valve 50, as described hereinbefore.

In the event of fluid pressure failure due to leaks or the like in the system branch 7, it is obvious that the fluid pressure in the main reservoir 3 will be thereby reduced in an attempt to replenish the depleted fluid pressure in the protected reservoir 16; therefore, when the fluid pressure in the main reservoir 3 is so reduced to the aforementioned predetermined minimum value, the control piston 82 is moved by the spring 88 to effect automatic actuation of the valve element 63 and establish pressure fluid communication between the inlet and outlet ports 37, 38 thereby effecting energization of the wheel brake assemblies connected therewith, as previously described. Meanwhile, the relay piston 54 is movable independently of the emergency member 90 in response to the fluid pressure established at the outlet port 38 to actuate the valve element 50 to its wide open position; however, since the protected reservoir 16 is depleted, as aforementioned, fluid pressure is not established at the outlet port 46.

In the event of fluid pressure failure due to leaks or the like in the system branch 6, it is obvious that the fluid pressure in the main reservoir 3 will also be reduced in an attempt to replenish the depleted fluid pressure in the protected reservoir 10; therefore, when the fluid pressure in the main reservoir 3 is so reduced to the aforementioned predetermined minimum value, the control piston 82 is moved by the spring 88 to concertedly drive the emergency member 90. This concerted downward movement initially engages the control piston valve seat 87 with the valve element 63 to effect actuation thereof; however, since the protected reservoir 10 is depleted, as aforementioned, fluid pressure is not established at the outlet port 38 or in the application chamber 61 to actuate the relay piston 54. Further downward movement of the control piston 82 drives the emergency member 90 independently of the relay piston 54 to initially engage the emergency member valve seat 91 with the valve element 50 closing the exhaust opening 51 thereof and isolating the outlet chamber 62a from the atmosphere and thereafter disengage said valve element from the housing valve seat 53 to establish pressure fluid communication between the inlet and outlet ports 45, 46. The established fluid pressure at the outlet port 46 acts on the area A of the relay piston 54 creating a force to urge said relay piston independently of said emergency member into abutment with the intermediate housing 28; therefore, since the emergency member opposed areas A;,, A are subjected to atmosphere, it is apparent that no reaction force is established in opposition to the compressive force of the spring 88 since the entire reaction force of the fluid pressure at the outlet port 46 acting on the relay piston area A is transferred to the housing. Further, it is also obvious that the compressive force of the spring 88 is unopposed by any other springs, such as for instance the relay piston return spring 56, since the relay piston 54 and emergency member 90 are movable completely independently of each other.

Referring now to FIG. 3, another control valve 109 is shown having substantially the same component parts and functioning in the system 1 in substantially the same manner as the previously described control valve 9 with the following exception.

In the control valve 109, an emergency member is sildably received in the intermediate housing bore 67 and the relay piston bore 59 having a valve seat 191 defined on the lower or free end thereof for operative engagement with the valve element 50. The upper end of the emergency member 190 is drivingly connected or integrally formed with the valve element 163, and an exhaust passage 192 is provided through said emergency member and valve element.

Under the aforementioned emergency conditions when the fluid pressure in the main and protected reservoirs 3, 10 are depleted, the control piston 82 is moved by the spring 88 to engage the valve seat 87 with the valve element 163 to effect actuation thereof; however, since the protected reservoir is depleted, fluid pressure is not established at the outlet port 38 or in the application chamber 61 to actuate the relay piston. Further concerted downward movement of the control piston 82 and valve element 163 drives the emergency member 190 independently of the relay piston 54 to initially engage the emergency member valve seat 191 with the valve element 50 closing the exhaust passages 51, 192 thereof and isolating the outlet chamber 62a from the atmosphere and thereafter disengage said valve element 50 from the housing valve seat to establish pressure fluid communication between the inlet and outlet ports 45, 46. The established fluid pressure at the outlet port 46 acts on the area A of the reaction piston 54 creating a force to urge said relay piston independently of said emergency member into abutment with the intermediate housing 28; therefore, since the emergency member opposed areas A A are subjected to atmosphere, it is apparent that no reaction force is established in opposition to the compressive force of the spring 88 since the entire reaction force of the fluid pressure at the outlet port 46 acting on the relay piston area A is transferred to the housing. Further, it is also obvious that the compressive force of the spring 88 is unopposed by any other springs, such as for instance the relay piston return spring 56, since the relay piston 54 and emergency member 190 are movable completely independently of each other.

From the foregoing, it is now apparent that novel control valves 9, 109 meeting the objects and advantages set out hereinbefore are provided and that changes or modifications as to the precise configurations, shapes or details of the constructions set forth by way of illustration may be made by those skilled in the art without departing from the spirit of the invention, as defined by the claims which follow.

The embodiments of the invention in Which an exclusive property or privilege is claimed are defined as follows:

1. A control valve comprising a housing having a pair of pressure fluid flow passages therein, a pair of application means movable in said housing and controlling said flow passages, one of said application means being movable in response to an applied force toward a position in one of said flow passages establishing pressure fluid flow therethrough and the other of said application means being movable in response to the established fluid pressure in said One flow passage toward a position in the other or" said flow passages establishing pressure fluid flow therethrough, and other means movable through said other application means and completely independently thereof to also control said other flow passage including a driven connection with said one application means, said other means being driven independently of said other application means in response to the applied force movement of said one application means toward a position in said other flow passage also establishing pressure fluid flow therethrough in the event of fluid pressure failure in said one flow passage.

2. The control valve according to claim 1 comprising a fluid pressure responsive area on only said other application means in said other flow passage, and abutment means between said housing and other application means to transfer to said housing the entire force of the fluid pressure established in said other flow passage and acting on said area upon the independent movement of said other means.

3. A control valve comprising a housing having a pair of pressure fluid flow passages therethrough, means movable in said housing for controlling one of said flow passages, said movable means being movable in response to an applied force toward a position in said one flow passage establishing pressure fluid flow therethrough, a pair of application means movable independently of each other in said housing, one of said application means having a control portion controlling the other of said flow passages, said one application means defining with said housing an expansible fluid pressure chamber in opposed relation with said other flow passage and connected in pressure fluid communication with said one flow passage, said one application means being movable independently of the other of said application means in response to the established fluid pressure in said one flow passage to move said control portion toward a position in said other flow passage establishing pressure fluid flow therethrough, said other application means including a portion movable in said one application means and extending through said chamber for driven connection with said movable member and another control portion movable through said first named control portion for controlling said other floW passage, said other application means being driven independently of said one application means in response to the applied force movement of said movable means to move said other control portion toward a position in said other flow passage establishing pressure fluid flow therethrough in the event of fluid pressure failure in said one flow passage.

4. A control valve comprising a housing having a pair of sets of ports therein, each of said port sets including inlet and outlet ports, a pair of valve means controlling pressure fluid communication between the inlet and outlet ports of said port sets, respectively, a pair of valve control members movable in said housing for operative engagement with said valve means, one of said valve control members being movable in response to an applied force to engage and move one of said valve means toward a position establishing pressure fluid communication between the inlet and outlet ports of one of said port sets, the other of said valve control members defining with said housing an expansible fluid pressure chamber connected in pressure fluid communication with the outlet port of said one port set, said other valve control member being movable in response to established fluid pressure at the outlet port of said one port set to engage and move the other of said valve means toward a position establishing pressure fluid communication between the inlet and outlet ports of the other of said port sets, and an emergency member movable in said other valve control member and completely independently thereof including a portion extending through said chamber for driven connection with said one valve control member and another portion for operative engagement with said other valve means, said emergency member being driven independently of said other valve control member in response to the applied force movement of said one valve control member to engage and actuate said other valve means in the event of fluid pressure failure at the outlet port of said one'port set.

5. The control valve according to claim 4 comprising a valve seat on said other valve control member for operative engagement with said other valve means, and another valve seat on the other portion of said emergency member for operative engagement with said other valve means, said emergency member being movable through said first named valve seat to engage said other valve seat with said other valve means and effect actuation thereof.

6. The control valve according to claim 4, wherein said other valve control member includes piston means movable in said housing and defining therewith said chamber, extension means on said piston means, a bore extending through said piston means and extension means, and a valve seat on said extension in circumscribing relation with said bore, said piston means being movable in response to the established fluid pressure at the outlet port of said one port set to engage said valve seat with said other valve means and effect actuation thereof, said emergency member being movable in said bore, and a free end portion on said emergency member defining another valve seat substantially concentric with said first named Valve seat and movable therethrough to engage and actuate said other valve means in response to the independent applied force movement of said emergency member.

7. The control valve according to claim 4 comprising a fluid pressure responsive area on only said other valve control member responsive to the fluid pressure established at the outlet port of said other port set, and abutment means between said other valve control member and housing for transferring to said housing the entire force of the fluid pressure established at the outlet port of said other port set upon the independent driven movement of said emergency member and acting on said area.

8. A control valve comprising a housing having a pair of sets of ports therein, each of said port sets including inlet and outlet ports, a pair of valve means controlling pressure fluid communication between the inlet and outlet ports of said port sets, respectively, a pair of valve control members mova'ble in said housing for operative engagement with said valve means, one of said valve control members being movable in response to an applied force to engage and move one of said valve means toward a position establishing pressure fluid communication between the inlet and outlet ports of one of said port sets, the other of said valve control members defining with said housing an expansible fluid pressure chamber connected in pressure fluid communication with the outlet port of said one port set, said other valve control member being movable in response to the established fluid pressure at the outlet port of said one port set to engage and move the other of said valve means toward a position establishing pressure fluid communication between the inlet and outlet ports of the other of said port sets, and said one valve means including means movable in said other valve control members and completely independently thereof for operative engagement with said other valve means, said last named means being movable independently of said other valve control member in response to the applied force movement of said one valve control member and one valve means to engage and actuate said other valve means in the event of fluid pressure failure at the outlet port of said one port set.

9. The control valve according to claim 8 comprising a valve seat on said other valve control member for operative engagement with said other valve means, said last named means being movable through said valve seat and defining another valve seat for operative engagement with said other valve means.

10. The control valve according to claim 8, wherein said other valve control member comprises piston means movable in said housing and defining therewith said chamber, extension means on said piston means, a bore extending through said piston means and extension means, and a valve seat, on said extension means in circumscribing relation with said bore, said piston means being movable in response to the established fluid pressure at the outlet port of said one port set to engage said valve seat with said other valve means and eflect actuation thereof, and said last named means including other extension means movable in said housing and said bore and extending through said chamber, and a free end portion on said other extension means defining another valve seat substantially concentric with said first named valve seat and movable therethrough to engage and actuate said other valve means in response to the applied force movement of said one valve control member and said one valve means upon the failure of fluid pressure at the outlet port of said one port set.

11. The control valve according to claim 10 comprising opposed fluid pressure responsive areas on only piston means respectively responsive to fluid pressures at the outlet ports of said one and other port sets, and abutment means between said piston means and housing for transferring to said housing the entire force of the fluid pressure established at the outlet port of said other port set and acting on the area responsive thereto upon the independent movement of said last named means to actuate said other valve means in the event of fluid pressure failure at the outlet port of said one port set.

References Cited UNITED STATES PATENTS 3,291,539 12/1966 Bueler 30352 MILTON BUCHLER, Primary Examiner.

I. MCLAUGHLIN, Assistant Examiner.

UNITED STATES PATENT OFFICE CERTIFICATE OF CORRECTION Patent No. 3,359,043 December 19, 1967 Joseph E. Papin It is hereby certified that error appears in the above numbered patent requiring correction and that the said Letters Patent should read as corrected below.

In the heading to the printed specification, lines 4 and 5, for "Tung-Sol Electric Inc., Newark, N. J., a corporation of Delaware" read Wagner Electric Corporation, South Bend, Ind. a corporation of Delaware Signed and sealed this 28th day of January 1969.

(SEAL) Attest:

Edward M. Fletcher, Jr. EDWARD J. BRENNER Attesting Officer Commissioner of Patents 

1. A CONTROL VALVE COMPRISING A HOUSING HAVING A PAIR OF PRESSURE FLUID FLOW PASSAGES THEREIN, A PAIR OF APPLICATION MEANS MOVABLE IN SAID HOUSING AND CONTROLLING SAID FLOW PASSAGES ONE OF SAID APPLICATION MEANS BEING MOVABLE IN RESPONSE TO AN APPLIED FORCE TOWARD A POSITION IN ONE OF SAID FLOW PASSAGES ESTABLISHING PRESSURE FLUID FLOW THERETHROUGH AND THE OTHER OF SAID APPLICATION MEANS BEING MOVABLE IN RESPONCE TO THE ESTABLISHED FLUID PRESSURE IN SAID ONE FLOW PASSAGE TOWARD A POSITION IN THE OTHER OF SAID FLOW PASSAGES ESTABLISHING PRESSURE FLUID FLOW THERETHROUGH, AND OTHER MEANS MOVABLE THROUGH SAID OTHER APPLICATION MEANS AND COMPLETELY INDEPENDENTLY THEREOF TO ALSO CONTROL SAID OTHER FLOW PASSAGE INCLUDING A DRIVEN CONNECTION WITH SAID ONE APPLICATION MEANS, SAID OTHER MEANS BEING DRIVEN INDEPENDENTLY OF SAID OTHER APPLICATION MEANS IN RESPONSE TO THE APPLIED FORCE MOVEMENT OF SAID ONE APPLICATION MEANS TOWARD A POSITION IN SAID OTHER FLOW PASSAGE ALSO ESTABLISHING PRESSURE FLUID FLOW THERETHROUGH IN THE EVENT OF FLUID PRESSURE IN SAID ONE FLOW PASSAGE. 